PISTON INTERNAL COMBUSTION ENGINE VARIABLE ACTION VALVE LIFTER SYSTEM

Abstract: Internal combustion engine variable valve lifter system inserted between the contact surface of a conventional in use mechanical or hydraulic type valve lifter (23), with the respective cam (24) of the camshaft, through which, with the variation of hydraulic means pressure applied on, the inside of the formed chamber (28), located proper elastic balls (25) is achieved the gradual variation of the respective valve operational characteristics (which variation concerning valves in a cylinder could be executed in a successive manner) in the medium and lower engine RPM's range.

Description: DESCRIPTION Piston Internal Combustion Engine variable action valve lifter system. FIELD OF THE INVENTION The invention refers to a new system and method that provides the capability to a valve lifter of a piston internal combu-! stion engine (I.C.E.) to act in a variable way on the respecti¬ ve valve, as well as the variation of its timing in general, namely the variation of the valve opening time moment, as well as the variation of the valve opening-valve closing time dura¬ tion. This variation is executed gradually. It is also possi¬ ble, with reference to similar valves of the same internal combustion engine cylinder, the gradual variation of one valve""s characteristics to follow at a predetermined time lapse the gradual variation of another valve's characteristics with the purpose of smoother improvement of the internal combustion engi¬ ne performance in the medium and lower operation RP range. BACKROUND OF THE INVENTION It is well known that conventional presently in use valve li- fter, mechanically or hydraulically adjusted, being constantly in contact with the respective cam of a rotating camshaft of an internal combustion engine, transmits the motion for the opening or closing of the respective valve with a stable manner, through the help of the valve spring. A further control of the valve motion is achieved according to Patent Number 4.765.288 and P.N. 4889084 through a valve mecha¬ nism, which has a basic idea the control of the pressure of a hydraulic means, being able to penetrate and come out from a chamber coming in between the respective cam of the internal combustion engine camshaft and the upper end of a movable small piston securely with the respective valve. The system requires an electromagnetic valve through which the control of the hydraulic means is achieved and a reservoir for- the returning hydraulic means. This reservoir is located out- side the electromagnetic valve or is part of the electromagnetic valve construction. A consequent of the above mentioned mecha- nis is the possibility of changing the operational characte¬ ristics of an internal combustion engine valve. In spite of that, the above mentioned mechanism, has the dis¬ advantage of requiring increased space between the valve end of the respective internal combustion engine cylinder and the corresponding cam, resulting in the need for a new cylinder- head design and the increase in production cost. Another disadvantage is also the fact, the complicated mecha¬ nism in conjuction with the mass of its components is creating obviously, inetria problems during the engine operation. Fi¬ nally the manufacturing cost of the mechanism multiplied by the number of the valves, is aggravating considerably the pro¬ duction cost of a motor. The present invention requires only a simple system for in- creasing and decreasing the pressure of a fluid, in a chamber enclosed inside the valve lifter type (mechanically or hydrau- lically adjusted) already in use in most motor models, manu¬ factured by various companies today, so that no additional cylinder head space is required, between the cam and the re- spective valve lifter, that would have resulted in the need of a new cylinder head design. The system can operate with the variation of the pressure of the oil supplied for internal combustion engine lubrication. It is also obvious, that no inertia problem is occuring during the operation of the engine and the manufacturing cost is si¬ milar to the cost of a hydraulic type valve lifter. The present invention offers an improvement in the effociency and the torque distribution of the internal combustion engine in the medium and lower operation RPM range, with the gradual reduction of the valve action but also with the succesive mo¬ vement of the valves of the respective cylinder, resulting in a further improvement of the engine torque distribution and consequently in fuel economy and in reduction of polluting emmissions. BRIEF DESCRIPTION OF DRAWINGS FIG.1: Shows the above mentioned system, where the contact surface between the valve lifter and the respective cam is able to move (in respect to the valve lifter) . The same figu¬ re shows in diagram the change in the valve operation with the help of the above mentioned system. FIG.2: Shows a variation of the above mentioned syste ,where the movement of the contact surface is executed along a fixed center of rotation. The same figure shows in diagram, the cha¬ nge in the valve operation, with the help of the above mentio¬ ned system. FIG.3: Shows the above mentioned system, where the contact surface of the valve lifter with the respective cam is fixed (without any ability to move in respect to the valve lifter) . The same figure shows in diagram, the change in the valve ope¬ ration, with the help of the above mentioned system. FIG.4: Shows a variation of the above mentioned system, where the change in the valve operation characteristics is achieved without the use of the elastic balls of the previous cases. FIG.5: Shows an application of the above mentioned system in a hydraulic type valve lifter. FIG.6: Shows an application of the above mentioned system where two supply ducts of the hydraulic means are used. FIG.7: Shows an application of the above-mentioned system in engines with side camshaft. DETAILED DESCRIPTION OF THE INVENTION Refering to FIG.1 we see an application of the variable action valve lifter system, which consists of the valve lifter (1), the movable part of the valve lifter (2) which comes in contact with the respective cam (3) , the elastic balls (4) the inner ring (5) in contact with the respective valve (6) . When the system is in contact with the cylindrical base of the cam, it has the shape shown in FIG.1 (a) . As the noncylindrical part of the cam starts to come in contact with the movable part of the valve lifter (2) produces a tilting and a movement of this part downwards while the elastic balls of this side are depressed up to the point their elasticity is allowing them to be compressed. Up to this point we have no movement downwards of the inner ring (5) and consequently of the valve (6) . The movement of the valve starts, when the first balls are alrea¬ dy completely compressed, and continues, as the edge of the cam moves towards the center of the valve lifter, up to the point, when all the balls are compressed, by the time the edge of the cam coincides with the center of the valve lifter. At this point we have the maximum lifting cam. Continuing the movement of the cam we see the return of the valve lifter in its initial position and consequently the closing of the valve, when the cylindrical base of the cam comes in contact with the valve ..lifter. The chamber between the parts (1) , (2) of the valve lifter and the inner ring (5) , where the elastic balls (4) are loca¬ ted can be filled with hydraulic means. By varying, with any possible way, the pressure of this hydraulic means inside the chamber (7) , we can influence the elastic behaviour of the ball (4) and consequently vary the operational characteristics of the system. Specifically: By increasing the pressure of the hydraulic means the elastic behaviour of the balls is reduced, as it is obvious, and consequently they will give in less as they will take, through the valve lifter, the pressure of the respective cam. By increasing gragually further the pressure of the hydraulic means, we can achieve a situation where the balls will behave practically as nonelastic and consequently the whole valve lifter will behave as a conventional valve lifter. We have the reverse procedure if we start gradually reducing the pressure of the hydraulic means. In this way we can achie¬ ve a gradual change in the operational characteristics of the valve lifter and consequently of the respective valve between an initial .(d) and final (c2) state, as shown in the diagram in FIG.1 (d) . The flowing in and out of the hydraulic means in and out the chamber (7) is achieved through the duct (8) and the circum- ferential groove (9). The lock (11) is serving the purpose of securing the whole system, after the assemply procedure is finished. The shape of the cam, the elastic characteristics of the balls, the characteristicsof the spring of the respe¬ ctive valve, as well as the varying pressure of the hydraulic means, are carefully calculated, so that each time the desi¬ red result is achieved. Refering to FIG.2 we see an application of the variable action valve lifter which consists of the valve lifter (12) , the mo¬ vable part of the valve lifter (13) , the cam (14) , the elastic balls (15) , the inner ring (16), the valve (17), the metallic ball (21) . The above mentioned application has a difference, that in the center of the valve lifter there is a metallic- ball (21) sea¬ ted in a respective size spherical recess in the inner ring (16) and the movable part of the valve lifter (13). Arround the metallic ball and inside the chamber (18) the elastic balls (15) are located. The system functions in the same man¬ ner described earlier, thus, the valve starts to move from the moment the elastic balls can't be compressed any more. The ela¬ stic behaviour of -these balls can also in this case vary exa¬ ctly in the same manner described previously (page 4,lines 18 - 32) . The oscilation of the movable part of the lifter on the metal¬ lic ball (21) results, in all cases of varying pressure inside the space (18) and consequently differing elastic behaviour of balls (15), in keeping constant the maximum valve lifting, since this is defined by the metallic ball, whose size is un- changable. This fact is clearly shown in the graph FIG.2(d) , where is shown the initial (d) and the final (c2) operational state of the respective valve. Refering to FIG.3 we see another application of the variable action valve lifter system, where the valve lifter is uniform, without the presence of a movable part. During the movement of the cam the whole valve lifter (23) moves downwards compres¬ sing the whole of elastics balls (25). The movement of the inner ring (26) and consequently the respective valve (27) starts only when the elastic balls are compressed in such a degree, so that their resistance in further compression is exceeding the resistance of the respective valve spring. In the same way described in the previous two cases, the varia¬ tion of the pressure of the hydraulic means inside the cha¬ mber (28) has a direct effect on the variation of the elastic behaviour of the balls (25) and consequently on the variation of the operational characteristics of the system. The flowing of the hydraulic means inside the chamber (28) is achieved through the duct (29) and the circumferencial groove (31) curved on the inner ring and (3) on the valve lifter, as shown in detail in Fig.3(a). Fig.3(d) shows the initial (d) and final (c2) operational state of the valve, achieved through the above mentioned system. In Fig.4 (a) we see another application of the variable action valve lifter system consisting of the valve lifter (33) the inner ring (36) , the chamber between those two (35) , the cam (34), the valve (37), the spring washer (38), the cylinder (39), the piston (40), the spring (41), the adjusting screw (42) and the washer (43) . In the chamber (35) there aren't any more elastic balls. The whole chamber is flooded with hydraulic means whose pressure can change. The flooding of this chamber is achieved through the duct (46) , the circumferencial grooves (45) on the valve lifter and (.44) on the inner ring and the duct (43) . When the non cylindrical part of the cam :starts to come in contact with the valve lifter (33) , the valve lifter gives in forcing the hydraulic means out from the chamber (35) through the ducts (43) and (46) into the cylinder (39) . In this way the piston (40) is forced by the hydraulic means and moves upwards. The travel of this movement depends,obvi¬ ously, on the characteristics of the spring (41). When the spring is completely compressed it does not allow any more the flowing o the hydraulic means in the cylinder (39) and consequently the further escape of hydraulic oil from the chamber (35)- of the valve lifter. In this way, while up to this point only the valve lifter (33) was moving, through the hydraulic means inside the chamber (35) , which has no escape route, the inner ring (36) is pushed and consequently the respective valve. As the edge of the cam passes the center of the valve lifter and moves away, the valve lifter (33) is free to move and is moving upwards with the help of the hydraulic means which is foreced by the spring (41) and the piston (40) out from the cylinder (39) and in the cha- ber (35) . From the above mentioned, it is clear that the valve movement begining moment, as well as the degree of the maximum lifting of the valve, depends on the elastic characteristic of the spring (41), which defines the amount of hydraulic means that is allowed to come out from the chamber (35) and enter the cylinder (39) . Consequently a control on the elastic behaviour of the spring (41) would allow us respectively the control on the operational characteristics of the valve. This control is made possible as follows: By increasing the pressure of the hydraulic means inside the duct (46) we have a flow of hydraulic means inside the cyli¬ nder (39) , which pushes the piston (40) and compresses the spring (41) in a length proportional to its pressure. Obvi¬ ously in this way the allowed compression of the spring through the flow of hydraulic means inaide the cylinder (39) , which is forced out. from the chamber (35) , because of the pressure from the cam action, is reduced. This fact means a smaller self travel for the valve lifter (33) ,an earlier opening of the valve, as well as an increase in the maximum cam lifting. With further increase in the pressure of the hydraulic means, we can achieve an even greater compression of spring (41) up to the point of complete compression. At this point,of course, the possibility for no further spring compression, means that hydraulic means cannot escape from chamber (35) , when the valve lifter if pushed by the cam, and consequently the beha¬ viour of the valve lifter is similar to a conventional one. We have the reverse procedure, when gradually we start redu¬ cing the pressure of the hydraulic means. An initial adjustment of the prestressing of spring (41) is possible through the adjusting screw (42) and washer (43) . The profile of the cam,the elastic characteristics of the spring (41), and the pressure of the hydraulic- eans are properly calculated, so that the desired result is achieved every time. We point out here, that the spring washer (38) is simply securing the continuous contact of the valve lifter with the respective valve, even when the motor is not running and does not play any other role, in the whole operation of the system. The width also of the circumferencial grooves (44) and (45) is properly calculated, so that, in every position of the valve lifter, during its travel in relation to the inner ring (36) , the ducts (43) and (46) are constantly in contact. An important modification of the above mentioned system is the possibility to achieve the change in the compression of the spring (41) (aiming each time in varying its elastic be- haviour) not through the variation of the pressure of the hydraulic means, as described previously, but through a pro¬ per adjusting screw, locaced on top of cylinder (39) (like the adjusting screw (42) shown on Fig. 4(a)) and which screw moving downwards gradually with the help of- an independent means (e.g. an electric motor) pushes-through the help of a washer as for example washer (43) and compresses spring (41) or moving upwards releases the spring. Refering to Fig. 4(b) we see a modification of the system just previously described, where instead of-cylinder (39) there is a pressure vessel (47) and in the place of spring (41) there is an elastic membrane filled with compressed air. The operation of this system is similar to the operation of the system previously described. Refering to Fig.6 we see an application of the variable action valve lifter system, which is described on page 5,lines 21-37 and page 6,pages 1-11, with the only difference that the valve lifter is of hydraulic type and not mechanical type. Refering to Fig.5 we see diagramatically the use of two hy¬ draulic means supply ducts, instead of one. This-can be used in the case of pairs for each valve type in every cylinder (two inlet valves and two exhaust valves) . The first duct supplies the hydraulic means to the valve lifters ^ of one inlet valve and of one exhaust valve and the second to the valve lifters of the other inlet and exhaust valve of the cylinder. Every variation in the pressure, inside the ducts, produces a variation of the characteristics of the respecti- ve valves, with which it is connected, according to what was described so far. In addition to that, if the variation of the hydraulic-means pressure, inside to one duct is executed with a properly calculated delay, in connection with the re¬ spective hydraulic means pressure variation, in the other duct, we achieve the change of the operational successive cha¬ racteristics of the similar valves in each cylinder, with the obvious result of an even smoother torque distribution in the medium and lower rpm operational range of the motor. Refering to Fig.7 we see an application of the variable action valve lifter system concerning side camshafts and consists of the respective valve lifter (49) (hydraulic type) the inner ring (50), the chamber between them (51), the elastic ball (52) . Variation of the hydraulic means pressure inside the chamber (51), produces the same results with those, of the various applications described so far.

Claims: CLAIMS 1. Variable action valve lifter system inserted, between the contact surface of a conventional in use, mechanical or hydraulic type valve lifter, with the respective cam of an internal combustion engine camshaft, and the end of the re- spective valve stem or the plunger of the hydraulic valve lifter, located inside the cylindrical body of one at least valve lifter, characterized by the following: a) It cooperates with at least one fixed cam of a conventio¬ nal camshaft, so that it can vary gradually the operational characteristics of the valve, achieving a gradual increase and smooth motor torque distribution, along its medium and lower operational RPM range, having also the possibility, this graduall variation of operational characteristics, of similar valves in a cylinder, to be executed in a succesive way (Fig. 1) , b) The contact surface of the valve lifter can be movable and oscilating during the contact with the respective"cam, inclined from the horizontal plane at an angle depended each time from the parameters of the hydraulic pressure applied on inserted elastic balls or elastic means, the profile of the respective cam and spring of the respective valve, and is coming back to the horizontal plane when it contacts the cylindrical part of the cam (Fig.l) , c)- Inside the cylindrical body (section) of- the valve lifter, there is an inner ring, fitted in the inner surface of the valve lifter, with the proper tolerance required for a fluid tight fit, being in contact with the end of- the re¬ spective valve stem or the plunger in the case of a hydrau¬ lic type valve lifter. In the--chamber, formed in this way between the inner ring and the bottom of the valve lifter, is increased a proper number of elastic balls of predetermi¬ ned elastic characteristics, whose degree of distortion is varying proportionally to the variation of the hydraulic pressure of a hydraulic means supplied in the above mentioned. chamber, through a properly shaped duct, and with the help of a means for the variation of the hydraulic pressure.Instead of the elastic balls any proper elastic means may be inserted (Fig.1) . 2. Variable action valve lifter system according to claim 1 characterized by the fact, that it is a variation of the above mentioned system, where the inner ring inside the valve lifter, as well as the bottom of the valve lifter have a sphe- rical recess each, in which is seated a metallic ball, which defines the fixed oscilation center of the movable contact surface of the valve lifter, during which (oscilation) is achieved the desired variation of the operational characteri¬ stics of the respective valve and consequently the improve- ment of the motor efficiensy in the medium and lower operatio¬ nal RPM range. (Fig.2) . 3. Variable action valve lifter system according to claim 1 characterized by the fact, that the contact surface of the valve lifter and the respective cam is fixed (surface of a conventional valve lifter) and the inner ring is movable, sliding inside the valve lifter, with the help of distorted balls or other proper elastic means, whose elastic behaviour is possible to change with the variation of- a hydraulic means pressure, inside the chamber formed between the inner ring and the bottom of the valve lifter. The action of the above mentioned system, in this case too, results the gradual va¬ riation of the operational characteristics of the respective valve, achieving a gradual increase and smooth motor torque distribution in the medium and lower operational RPM range, having also the capability, this gradual change of the opera¬ tional characteristics of -similar valves in the same cylinder to be executed in a successive manner. (.Fig.3) . 4. Variable action valve lifter system according to claims 1 and 2, characterized by the fact, that as a means for its variable operation is • required a) the motor lubrication oil as hydraulic means-and b) a number of elastic balls of pro¬ per composition and carefully selected elastic characteristics or any other proper elastic means with the required elastic characteristics. 5. Variable action valve lifter system, according to claims 1, 2, 3, 4 characterized by the fact, that the above mentioned system operates exclusively and only inside the cylindrical chamber of a conventional in use mechanical or hydraulic ty¬ pe valve lifter. 6. Variable action valve lifter system, according to claims 1, 4 and 5 characterized by the fact, that the contact sur¬ face of the valve lifter with the respective cam, is capable of being movable and oscilating, during the movement of the cam, and the variation of the hydraulic means pressure on the elastic balls, returning to the horizontal plane, during its contact with the cylindrical base of the cam. 7. Variable action valve lifter system, according to claims 1, 2, 3, 4, 5, 6 characterized by the fact, that the variation of the hydraulic pressure, inside the above mentioned valve lifter chamber, achieved with the help of any proper means, in the hydraulic means supply duct in this chamber, results in the varied distortion of the inserted in this chamber ela¬ stic balls or other elastic means, located between the sli¬ ding inner ring and the fixed valve lifter bottom, achieving a gradual and smooth variation of the respective valve opera- tional characteristics. A further improvement of the above mentioned valve operation is achieved through the oscilating surface of the valve lifter (claim 1) and consequently its inclinations from the horizontal plane during the movement, so that a more drastic change of the respective valve opera- tional characteristics is achieved. 8. Variable action valve lifter system, according to claim 1, 2 and-3 characterized by the fact, that a second hydraulic means supply duct is available, through which the above des¬ cribed pressure variation in the considered system can follow, on properly calculated time lapse, the pressure variation in the other duct, so;that the gradual change of a valve opera¬ tional characteristics in a cylinder - connected with the one duct - is achieved in a successive manner in relation to the gradual change of the similar valve operational characteristics in the same cylinder - connected with the second duct,- with the result, the capability of an even smoother motor torque distribution in the medium and lower operational RPM range (Fig.6) . It is obvious that the efficiency of the engine in the higher operational RPM range, depends in any case on the selection of the proper profile of the fixed cam of the conventional engine camshaft. 9. A variable action valve lifter system characterized by the fact, that it suggests a variation in the embodiment of claim 3, according to which in the chamber formed between the bottom of the valve lifter or the end of the plunger,in the case of hydraulic type valve lifter, is introduced only the hydraulic means supplied for the engine lubrication and which, through a duct and properly curved on the valve lifter and inner ring circumferencial grooves, floods and chamber inside the valve lifter. In a carefully selected location on the fluid supply,duct, a pressure vessel is connected, contai¬ ning an elastic membrane filled with pressured-air, through which with-the variation of the hydraulic pressure, the same requirements-of claim 1 and 3 are achieved, namely the gra¬ dual change of the respective valve operational characteri- sties and the change of the operational characteristics of similar valves inside the same cylinder in a successive order, The same results are achieved, if instead of the pressure vessel with pressured air .is placed a small hollow cylinder filled with the fluid, having into it a proper spring, with a small piston moving, with the variation of hydraulic pres¬ sure. In this-*case instead of a means for varying the hydrau¬ lic pressure, it is possible to place on the upper part of the cylinder an adjusting screw, which by turning in a gra¬ dual way, with the help of any means, forces the spring towards the direction, achieving the gradual variation of the spring towards the direction of compression or releases it during its turning on the opposite direction, achieving the gradual variation of the spring compression inside the cy- linder-(Fig. 4a, 4b).

Inventors: VALASOPOYLOS CHRISTOS, VALASOPOYLOS, CHRISTOS
Applicants: VALASOPOYLOS CHRISTOS, VALASOPOYLOS, CHRISTOS
Application year: 1994
Main classification: F01L13
IPC codes: F01L1, F01L9, F01L13